Gravity-driven gas-liquid circulation device

ABSTRACT

The present invention provides a gravity-driven gas-liquid circulation device, comprising a condensation unit and an evaporation unit. The condensation unit has an end connected to a gaseous phase input tube and another end connected to a liquid phase output tube. The evaporation unit comprises a thermally conductive base for contact with an external high-temperature device, a plurality of fins integrally formed on the thermally conductive base, and an integrally formed sealing housing provided on the thermally conductive base and enclosing the fins, wherein the integrally formed sealing housing is provided with a gas outlet hole and a liquid inlet hole, the gas outlet hole is lower than the gaseous phase input tube and is connected to an end of the gaseous phase input tube in order to guide a high-temperature gaseous-state working fluid through the gaseous phase input tube to the condensation unit, and the liquid inlet hole is level with or lower than the liquid phase output tube and is connected to an end of the liquid phase output tube in order to receive a liquid-state working fluid, allowing a force of gravity acting on the liquid-state working fluid to provide a siphoning force and thereby cause circulation of the liquid-state working fluid and the gaseous-state working fluid.

BACKGROUND OF THE INVENTION 1. Technical Field

The present invention relates to a gas-liquid circulation device andmore particularly to a miniaturized gravity-driven gas-liquidcirculation device for use in an electronic product.

2. Description of Related Art

Electronic equipment is generally provided with a central processingunit (CPU) for processing commands and software data. The computationspeed and data transfer rate of a piece of electronic equipment hinge onthe performance of its CPU.

A CPU can maintain its performance or capacity at a reasonable level inmost cases. If, however, the heat generated by a CPU cannot bedissipated effectively, the CPU may be overheated, and the electronicequipment using the CPU may eventually slow down or even stop working asa result. The high temperature of the overheated CPU may also damage theneighboring electronic components such that the service life of theelectronic equipment is cut short. It is therefore imperative to use asuitable method or technique to cool a CPU sufficiently and therebymaintain its normal operation.

One typical technique for cooling the CPU of a piece of electronicequipment is to provide the electronic equipment with a built-in fan,the objective being to generate an air flow that helps bring down thetemperature of the CPU. However, the cooling effect of the fan will becompromised when ambient temperature is high. Another cooling techniqueinvolves the use of a cooling agent or refrigerant such as water.

According to the above, the conventional methods for cooling a CPU stillleave room for improvement. The inventor of the present inventionthought it necessary to devise a novel method for cooling a CPU.

BRIEF SUMMARY OF THE INVENTION

The primary objective of the present invention is to provide aminiaturized gas-liquid circulation device that is suitable for use inelectronic equipment.

In order to achieve the above objective, the present invention providesa gravity-driven gas-liquid circulation device, comprising acondensation unit and an evaporation unit. The condensation unit has anend connected to a gaseous phase input tube and another end connected toa liquid phase output tube. The evaporation unit comprises a thermallyconductive base for contact with an external high-temperature device, aplurality of fins integrally formed on the thermally conductive base,and an integrally formed scaling housing provided on the thermallyconductive base and enclosing the fins, wherein the integrally formedsealing housing is provided with a gas outlet hole and a liquid inlethole, the gas outlet hole is lower than the gaseous phase input tube andis connected to an end of the gaseous phase input tube in order to guidea high-temperature gaseous-state working fluid through the gaseous phaseinput tube to the condensation unit, and the liquid inlet hole is levelwith or lower than the liquid phase output tube and is connected to anend of the liquid phase output tube in order to receive a liquid-stateworking fluid, allowing a force of gravity acting on the liquid-stateworking fluid to provide a siphoning force and thereby cause circulationof the liquid-state working fluid and the gaseous-state working fluid.

Furthermore, the thermally conductive base is provided thereon with areinforcement member, wherein the reinforcement member is clampedvertically between the integrally formed sealing housing and thethermally conductive base and serves to increase the compressivestrength.

Furthermore, the reinforcement member is provided with at least onethrough hole and/or at least one aperture to enable passage of theliquid-state working fluid.

Furthermore, the integrally formed sealing housing includes a firsthousing portion and a second housing portion. The first housing portionis provided on the thermally conductive base and encloses the fins. Thesecond housing portion is integrally formed with, and lies on top of,the first housing portion.

Furthermore, the top sides of the tins are higher than the bottom edge,and lower than the top edge, of the liquid inlet hole or are higher thanthe top edge of the liquid inlet hole.

Furthermore, the gas outlet hole has a larger hole diameter than theliquid inlet hole.

Furthermore, the spacing between each two adjacent fins forms a flowchannel, and the spacing ranges from 0.2 mm to 1 mm.

Furthermore, the liquid inlet hole is in alignment with the flowchannels.

Furthermore, the fins are integrally formed on the thermally conductivebase by a relieving means.

Furthermore, each fin has a thickness ranging from 0.2 mm to 1 mm.

Furthermore, the condensation unit comprises a front condensationassembly, a rear condensation assembly, and a plurality of heatdissipation fins. The front condensation assembly comprises a front leftflow tube, a front right flow tube, and a plurality of front heatdissipation tubes. The front left flow tube and the front right flowtube are provided on two opposite lateral sides of the frontcondensation assembly respectively and are connected to the gaseousphase input tube and the liquid phase output tube respectively. Thefront heat dissipation tubes are in communication with the front leftflow tube and the front right flow tube and are vertically spaced apart.The rear condensation assembly comprises a rear left flow tube, a rearright flow tube, and a plurality of rear heat dissipation tubes. Therear left flow tube and the rear right flow tube are provided on twoopposite lateral sides of the rear condensation assembly respectively.The rear heat dissipation tubes are in communication with the rear leftflow tube and the rear right flow tube and are vertically spaced apart.Gaps between the rear heat dissipation tubes and gaps between the frontheat dissipation tubes correspond to each other and jointly form aplurality of through grooves. The heat dissipation fins are in contactwith surfaces of the front heat dissipation tubes and surfaces of therear heat dissipation tubes to enable heat exchange between the heatdissipation fins and the heat dissipation tubes. The front left flowtube and the rear left flow tube are separately formed. The front rightflow tube and the rear right flow tube are separately formed.

Furthermore, the condensation unit comprises a front condensationassembly, a rear condensation assembly, and a plurality of heatdissipation fins. The front condensation assembly comprises a front leftflow tube, a front right flow tube, and a plurality of front heatdissipation tubes. The front left flow tube and the front right flowtube are provided on two opposite lateral sides of the frontcondensation assembly respectively and are connected to the gaseousphase input tube and the liquid phase output tube respectively. Thefront heat dissipation tubes are in communication with the front leftflow tube and the front right flow tube and are vertically spaced apart.The rear condensation assembly comprises a rear left flow tube, a rearright flow tube, and a plurality of rear heat dissipation tubes. Therear left flow tube and the rear right flow tube are provided on twoopposite lateral sides of the rear condensation assembly respectively.The rear heat dissipation tubes are in communication with the rear leftflow tube and the rear right flow tube and are vertically spaced apart.Gaps between the rear heat dissipation tubes and gaps between the frontheat dissipation tubes correspond to each other and jointly form aplurality of through grooves. The heat dissipation fins are in contactwith surfaces of the front heat dissipation tubes and surfaces of therear heat dissipation tubes to enable heat exchange between the heatdissipation fins and the heat dissipation tubes. The front left flowtube and the rear left flow tube are jointly formed by two stampedplates. The front right flow tube and the rear right flow tube arejointly formed by two stamped plates.

Furthermore, at least one left opening is provided between the frontleft flow tube and the rear left flow tube. At least one right openingis provided between the front right flow tube and the rear right flowtube. The left opening and the right opening are diagonally arrangedwith respect to each other, wherein the bottom side of the left openingis higher than the top side of the right opening.

Furthermore, both the front heat dissipation tube and the rear heatdissipation tube have a flattened configuration.

Furthermore, the front heat dissipation tube is provided therein with aplurality of supporting ribs, which extend through the front heatdissipation tube. The rear heat dissipation tube is provided thereinwith a plurality of supporting ribs, which extend through the rear heatdissipation tube.

Furthermore, a plurality of microstructures are provided on the surfaceof each heat dissipation fin to increase the area of contact betweeneach heat dissipation fin and air.

Furthermore, the heat dissipation fins have a corrugated configurationor a serrated configuration.

Furthermore, the condensation unit includes a plurality of condensationplate assemblies and a plurality of heat dissipation fins. Thecondensation plate assemblies are vertically spaced apart. The heatdissipation fins are inserted between the condensation plate assembliesand are therefore also spaced apart from one another. Each condensationplate assembly is provided with a left flow tube on the left side, aright flow tube on the right side, and a flow passage in communicationwith the left flow tube and the right flow tube, wherein the left flowtube and the right flow tube are connected to the gaseous phase inputtube and the liquid phase output tube respectively.

Furthermore, each condensation plate assembly is formed by two metalplates, wherein each metal plate is provided with a plurality ofprotruding structures on the side facing the flow passage in order toincrease the strength of the condensation plate assembly.

Comparing to the conventional techniques, the present invention has thefollowing advantages:

The gas-liquid circulation device disclosed herein is provided with acondensation unit and an evaporation unit that utilize not only thephase change of a working fluid to cool an electronic product (i.e. thephase change taking place while the working fluid is changed between aheat-absorbing state and a heat-releasing state), but also the force ofgravity acting on the working fluid to enable continuous operation ofthe gas-liquid circulation device, thereby saving the cost and spaceotherwise required for installing an electromechanical driving device.

BRIEF DESCRIPTION OF THE SEVERAL VIEWS OF THE DRAWINGS

FIG. 1 is a perspective view of the gravity-driven gas-liquidcirculation device of the present invention.

FIG. 2 is a sectional view of the front condensation assembly accordingto the first embodiment of the condensation unit of the presentinvention.

FIG. 3 is a sectional view of the rear condensation assembly accordingto the first embodiment of the condensation unit of the presentinvention.

FIG. 4 is a perspective view of the heat dissipation fin according tothe first embodiment of the condensation unit of the present invention.

FIG. 5 is a perspective view of the front heat dissipation tubeaccording to the first embodiment of the condensation unit of thepresent invention.

FIG. 6 is a perspective view of the evaporation unit of the presentinvention.

FIG. 7 is the sectional view (I) of the evaporation unit of the presentinvention.

FIG. 8 is the sectional view (II) of the evaporation unit of the presentinvention.

FIG. 9 is a schematic circulation diagram of the gravity-drivengas-liquid circulation device of the present invention.

FIG. 10 is a perspective view of the second embodiment of thecondensation unit of the present invention.

FIG. 11 is a sectional view of the front condensation assembly accordingto the second embodiment of the condensation unit of the presentinvention.

FIG. 12 is a sectional view of the rear condensation assembly accordingto the second embodiment of the condensation unit of the presentinvention.

FIG. 13 is an assembled perspective view according to the thirdembodiment of the condensation unit of the present invention.

FIG. 14 is an exploded perspective view according to the thirdembodiment of the condensation unit of the present invention.

DETAILED DESCRIPTION OF THE INVENTION

The details and technical solution of the present invention arehereunder described with reference to accompanying drawings. Forillustrative sake, the accompanying drawings are not drawn to scale. Theaccompanying drawings and the scale thereof are not restrictive of thepresent invention.

Please refer to FIG. 1 for a perspective view of the gravity-drivengas-liquid circulation device of the present invention.

The gravity-driven gas-liquid circulation device 100 shown in FIG. 1 isconfigured for use mainly in the fields of optics, communications, dataprocessing, servers, and so on where high-heat laminated circuits aretypically required. The present invention can be applied to suchelectronic products as servers, data displays, remote radio units (RRUs)for communication purposes, artificial intelligence (AI) devices,display chips, and laser chips to provide a cooling/heat dissipationeffect through conduction-, convection-, or material-based heatexchange. The gas-liquid circulation device of the present invention isintended to dissipate heat from an electronic product via a continuouslycirculated working fluid that is driven by the force of gravity actingon the working fluid itself, thereby saving the cost and space otherwiserequired to drive the circulation electromechanically.

The gravity-driven gas-liquid circulation device 100 includes acondensation unit 10A and an evaporation unit 20A. A working fluid iscirculated through the two units while undergoing a cyclic change ofphase, which occurs when the working fluid is changed between aheat-absorbing state and a heat-releasing state. The phase change helpscool down the electronic product to which the gravity-driven gas-liquidcirculation device 100 is applied, lest the electronic components of theproduct be damaged, or the performance of the product be lowered, due toprolonged exposure to high heat.

Please refer to FIG. 2 and FIG. 3 for sectional views respectively ofthe front and rear condensation assemblies of the condensation unit ofthe present invention.

In this embodiment, the condensation unit 10A is connected to a gaseousphase input tube AT at one end and a liquid phase output tube WT atanother end. The condensation unit 10A includes a front condensationassembly 11A, a rear condensation assembly 12A, and a plurality of heatdissipation fins 13A. The front condensation assembly 11A includes afront left flow tube 111A, a front right flow tube 112A, and a pluralityof front heat dissipation tubes 113A in communication with the frontleft flow tube 111A and the front right flow tube 112A. The front leftflow tube 111A and the front right flow tube 112A are provided on thetwo opposite lateral sides of the front condensation assembly 11Arespectively and are connected to the gaseous phase input tube AT andthe liquid phase output tube WT respectively. The front heat dissipationtubes 113A are vertically spaced apart. The rear condensation assembly12A is parallel to the front condensation assembly 11A and includes arear left flow tube 121A, a rear right flow tube 122A, and a pluralityof rear heat dissipation tubes 123A in communication with the rear leftflow tube 121A and the rear right flow tube 122A. The rear left flowtube 121A and the rear right flow tube 122A are provided on the twoopposite lateral sides of the rear condensation assembly 12Arespectively. The rear heat dissipation tubes 123A are vertically spacedapart. The gaps between the rear heat dissipation tubes 123A and thosebetween the front heat dissipation tubes 113A correspond to each otherand jointly form a plurality of through grooves GA.

The front left flow tube 11A and the rear left flow tube 121A areseparately formed, and so are the front right flow tube 112A and therear right flow tube 122A. The two flow tubes on either lateral side ofthe condensation unit 10A are fixedly coupled to each other by a pair ofsealing covers 114A (one on top and the other at the bottom) to increasethe compressive strength of the flow tubes. The front left flow tube111A, the front right flow tube 112A, the rear left flow tube 121A, andthe rear right flow tube 122A are generally square tubes, with the sidesfacing diametrically away from the front heat dissipation tubes 113A (orthe rear heat dissipation tubes 123A) having an outwardly protruding,(circularly) curved shape to allow more efficient use of the spaceinside the flow tubes.

To enable communication between the front condensation assembly 11A andthe rear condensation assembly 12A, at least one left opening LO isprovided between the front left flow tube 111A and the rear left flowtube 121A, and at least one right opening RO is provided between thefront right flow tube 112A and the rear right flow tube 122A. In thepreferred embodiment shown in FIG. 1, a linking element 115A is providedbetween the front left flow tube 111A and the rear left flow tube 121Aand is aligned, and in communication, with the left opening LO so as toconnect, and allow communication between, the flow tubes. Similarly, alinking element (not shown) is provided between the front right flowtube 112A and the rear right flow tube 122A and is aligned, and incommunication, with the right opening RO. As shown in FIG. 2, there isone left opening LO and one right opening RO, and the two openings arerectangular openings diagonally arranged with respect to each other,wherein the bottom side of the left opening LO is higher than the topside of the right opening RO. The area of the left opening LO is largerthan that of the right opening RO to enable rapid input and slow outputof the working fluid. It should be pointed out, however, that theopenings described above serve only as an example; the present inventionimposes no limitation on the number or shapes of those openings.

Please refer to FIG. 4 for a perspective view of a heat dissipation finin the condensation unit of the present invention.

The heat dissipation fins 13A are inserted in the through grooves GArespectively and extend through the front condensation assembly 11A andthe rear condensation assembly 12A. The heat dissipation fins 13A are incontact with the surfaces of the front heat dissipation tubes 113A andof the rear heat dissipation tubes 123A so that heat exchange can takeplace between the heat dissipation fins 13A and the heat dissipationtubes 113A and 123A. The heat dissipation fins 13A may have a corrugatedconfiguration, a serrated configuration, or any other configurationachievable by bending a metal plate. Each heat dissipation fin 13A has aheight D1 ranging from 4 mm to 8 mm and a length D2 ranging from 12 mmto 60 mm. The distance D3 between each two adjacent bends of each heatdissipation fin 13A ranges from 2 mm to 4 mm. There are a plurality ofmicrostructures 131A on the surface of each heat dissipation fin 13A.The microstructures 131A may extend outward or inward with respect tothe heat dissipation fins 13A to increase the area of contact betweeneach heat dissipation fin 13A and air, thereby enhancing the efficiencyof heat dissipation. 10052 j Please refer to FIG. 5 for a perspectiveview of a front heat dissipation tube in the condensation unit of thepresent invention.

As shown in FIG. 5, the front heat dissipation tube 113A has a flattenedconfiguration. The two ends of the front heat dissipation tube 113A areinserted in the front left flow tube 111A and the front right flow tube112A respectively to connect the two flow tubes together. The front heatdissipation tube 113A has a height D4 ranging from 1 mm to 2 mm tofacilitate passage of, and allow sufficient heat absorption by, theworking fluid. The front heat dissipation tube 113A has a width D5ranging from 12 mm to 40 mm so as to provide a relatively large heatdissipation area that enhances contact, and hence heat exchange, withair and the adjacent heat dissipation fins 13A. The front heatdissipation tube 113A is provided therein with a plurality of supportingribs R, which extend through the front heat dissipation tube 113A. Thenumber of the supporting ribs R may range from the value of one half ofthe width (in millimeter) of the front heat dissipation tube 113A to thevalue of the full width (in millimeter) of the front heat dissipationtube 113A. For example, when the width of the front heat dissipationtube 113A is 12 mm, there may be 6 to 12 supporting ribs R forreinforcing, and thereby preventing deformation of, the front heatdissipation tube 113A. The rear heat dissipation tubes 123A in thepresent invention are structurally identical to the front heatdissipation tubes 113A and therefore will not be described or shownrepeatedly.

Please refer to FIG. 6 to FIG. 8 in conjunction with FIG. 1, whereinFIG. 6 to FIG. 8 respectively show a perspective view and two differentsectional views of the evaporation unit of the present invention.

The evaporation unit 20A includes a thermally conductive base 21A forcontact with a high-temperature device, a plurality of fins 22Aintegrally formed on the thermally conductive base 21A, and anintegrally formed sealing housing 23A provided on the thermallyconductive base 21A to enclose the fins 22A. In this preferredembodiment, the thermally conductive base 21A, the fins 22A, and theintegrally formed sealing housing 23A are made of aluminum or copper.The integrally formed sealing housing 23A includes a first housingportion 231A and a second housing portion 232A. The first housingportion 231A is provided on the thermally conductive base 21A andencloses the fins 22A. The second housing portion 232A is integrallyformed with, and lies on top of, the first housing portion 231A. Theinterior space of the second housing portion 232A is smaller than thatof the first housing portion 231A to accelerate the working fluid. Thethermally conductive base 21A is provided with a plurality of lockingholes 211A for securing the evaporation unit 20A to a high-temperaturedevice.

The integrally formed sealing housing 23A is provided with a gas outlethole 233A, which is lower than the gaseous phase input tube AT and isconnected to one end of the gaseous phase input tube AT in order toguide the high-temperature gaseous-state working fluid through thegaseous phase input tube AT to the condensation unit 10A. The integrallyformed scaling housing 23A is also provided with a liquid inlet hole234A, which is level with or lower than the liquid phase output tube WTand is connected to one end of the liquid phase output tube WT in orderto receive the liquid-state working fluid. The force of gravity actingon the liquid-state working fluid will provide a siphoning force thatcauses circulation of the working fluid, thereby enabling thegravity-driven gas-liquid circulation device 100 to operate continuouslywithout being driven by an electromechanical means. In this preferredembodiment, the gas outlet hole 233A has a larger hole diameter than theliquid inlet hole 234A to make it easier for the force of gravity actingon the liquid-state working fluid to serve as a driving force of thegravity-driven gas-liquid circulation device 100.

The fins 22A are integrally formed on the thermally conductive base 21Aby a relieving means. Each fin 22A has a thickness ranging from 0.2 mmto 1 mm to facilitate rapid heat exchange with the liquid-state workingfluid. The spacing S between each two adjacent fins 22A forms a flowchannel 221A. The spacing S ranges from 0.2 mm to 1 mm so that theliquid-state working fluid can flow through the flow channels 221A withease to carry out heat exchange with the fins 22A sufficiently.

The liquid inlet hole 234A is in alignment with the flow channels 221A.The top sides H of the fins 22A may be higher than the bottom edge, andlower than the top edge, of the liquid inlet hole 234A or be higher thanthe top edge of the liquid inlet hole 234A, the objective being to allowas much liquid-state working fluid as possible to flow through the flowchannels 221A and thereby increase the heat absorption efficiency of theevaporation unit 20A.

The thermally conductive base 21A is provided thereon with areinforcement member 24A. The reinforcement member 24A is clampedvertically between the integrally formed sealing housing 23A and thethermally conductive base 21A and serves to increase the compressivestrength, and thereby prevent deformation of, the evaporation unit 20A.The reinforcement member 24A is provided with at least one through hole241A and at least one aperture 242A to enable passage of theliquid-state working fluid. Or, the reinforcement member 24A may haveonly the through hole(s) 241A or the aperture(s) 242A; the presentinvention has no limitation in this regard.

Please refer to FIG. 9 for a schematic circulation diagram of thegravity-driven gas-liquid circulation device of the present invention.

The liquid-state working fluid in the condensation unit 10A is guidedinto the evaporation unit 20A through the liquid phase output tube WT.Meanwhile, the force of gravity acting on the liquid-state working fluidprovides a siphoning force such that the gaseous-state working fluid inthe evaporation unit 20A is driven into the condensation unit 10Athrough the gaseous phase input tube AT. Thus, the gravity-drivengas-liquid circulation device 100 forms a continuous heat exchange cyclewithout having to be driven by an electromechanical means.

The following paragraphs describe the second preferred embodiment of thecondensation unit of the disclosed gravity-driven gas-liquid circulationdevice. The second embodiment is different from the foregoing embodimentonly in the structure of the flow tubes, so the remaining structures ofthe condensation unit, as well as the evaporation unit, will not bedescribed repeatedly.

Please refer to FIG. 10 to FIG. 12 respectively for a perspective viewof the second embodiment of the condensation unit of the presentinvention, a sectional view of the front condensation assembly of thecondensation unit, and a sectional view of the rear condensationassembly of the condensation unit.

As shown in FIG. 10 to FIG. 12, the condensation unit 10B includes afront condensation assembly 11B, a rear condensation assembly 12B, and aplurality of heat dissipation fins 13B. The front condensation assembly11B includes a front left flow tube 111B, a front right flow tube 112B,and a plurality of front heat dissipation tubes 113B in communicationwith the front left flow tube 111B and the front right flow tube 112B.The front left flow tube 111B and the front right flow tube 112B areprovided on the two opposite lateral sides of the front condensationassembly 11B respectively and are connected to the gaseous phase inputtube and the liquid phase output tube respectively. The front heatdissipation tubes 113B are vertically spaced apart. The rearcondensation assembly 12B is parallel to the front condensation assembly11B and includes a rear left flow tube 121B, a rear right flow tube122B, and a plurality of rear heat dissipation tubes 123B incommunication with the rear left flow tube 121B and the rear right flowtube 122B. The rear left flow tube 121B and the rear right flow tube122B are provided on the two opposite lateral sides of the rearcondensation assembly 12B respectively. The rear heat dissipation tubes123B are vertically spaced apart. The gaps between the rear heatdissipation tubes 123B and those between the front heat dissipationtubes 113B correspond to each other and jointly form a plurality ofthrough grooves GB.

The front left flow tube 111B and the rear left flow tube 121B arejointly formed by two stamped plates, including an M-shaped stampedplate and a square U-shaped stamped plate. The front right flow tube112B and the rear right flow tube 122B are also jointly formed by anM-shaped stamped plate and a square U-shaped stamped plate. The stampedplates are intended to increase the compressive strength of the flowtubes. The two flow tubes on either lateral side of the condensationunit 10B are provided with a pair of scaling covers 114B (one on top andthe other at the bottom). The front left flow tube 111B, the front rightflow tube 112B, the rear left flow tube 121B, and the rear right flowtube 122B have an outwardly protruding, (circularly) curved shape on thesides facing diametrically away from the front heat dissipation tubes113B or the rear heat dissipation tubes 123B, in order to allow moreefficient use of the space inside the flow tubes.

The heat dissipation fins 13B are inserted in the through grooves GBrespectively and extend through the front condensation assembly 11B andthe rear condensation assembly 12B. The heat dissipation fins 13B are incontact with the surfaces of the front heat dissipation tubes 113B andof the rear heat dissipation tubes 123B so that heat exchange can takeplace between the heat dissipation fins 13B and the heat dissipationtubes 113B and 123B. The heat dissipation fins 13B may have a corrugatedconfiguration, a serrated configuration, or any other configurationachievable by bending a metal plate. There are a plurality ofmicrostructures on the surface of each heat dissipation fin 13B. Themicrostructures may extend outward or inward with respect to the heatdissipation fins 13B to increase the area of contact between each heatdissipation fin 13B and air, thereby enhancing the efficiency of heatdissipation.

To enable communication between the front condensation assembly 11B andthe rear condensation assembly 12B, at least one left opening LO1 isprovided between the front left flow tube 111B and the rear left flowtube 121B, and at least one right opening RO1 is provided between thefront right flow tube 112B and the rear right flow tube 122B. In thisembodiment, there is one left opening LO1 and one right opening RO1, andthe two openings are diagonally arranged with respect to each other,wherein the bottom side of the left opening LO1 is higher than the topside of the right opening RO1. It should be pointed out, however, thatthe openings described above serve only as an example; the presentinvention imposes no limitation on the number or shapes of thoseopenings.

The following paragraphs describe the third preferred embodiment of thecondensation unit of the disclosed gravity-driven gas-liquid circulationdevice. The third embodiment is structurally different from the previoustwo embodiments, and yet the corresponding evaporation unit is the sameas those for use with the foregoing two embodiments (and hence will notbe described repeatedly).

Please refer to FIG. 13 and FIG. 14 respectively for an assembledperspective view and an exploded perspective view of the thirdembodiment of the condensation unit of the present invention.

As shown in FIG. 13 and FIG. 14, the condensation unit 10C includes aplurality of condensation plate assemblies 11C and a plurality of heatdissipation fins 12C. The condensation plate assemblies 11C arevertically spaced apart. The heat dissipation fins 12C are insertedbetween the condensation plate assemblies 11C and are therefore alsospaced apart from one another. Each condensation plate assembly 11C isprovided with a left flow tube 111C on the left side, a right flow tube112C on the right side, and a flow passage 113C in communication withthe left flow tube 111C and the right flow tube 112C to allow passage ofthe gaseous-state working fluid, wherein the left flow tube 111C and theright flow tube 112C are connected to the gaseous phase input tube andthe liquid phase output tube respectively.

Each heat dissipation fin 12C is inserted between, and in contact withthe surfaces of, two adjacent condensation plate assemblies 11C toenable heat exchange between the heat dissipation fin 12C and the twocondensation plate assemblies 11C. The heat dissipation fins 12C mayhave a corrugated configuration, a serrated configuration, or any otherconfiguration achievable by bending a metal plate. There are a pluralityof microstructures on the surface of each heat dissipation fin 12C. Themicrostructures may extend outward or inward with respect to the heatdissipation fins 12C to increase the area of contact between each heatdissipation fin 12C and air, thereby enhancing the efficiency of heatdissipation.

Each condensation plate assembly 11C is formed by two metal plates P,wherein each metal plate P is provided with a plurality of protrudingstructures P on the side facing the flow passage 113C in order toincrease the strength of the condensation plate assembly 11C. Theprotruding structures P1 of each metal plate P are formed by stampingthe metal plate P and are preferably cylindrical or dome-shaped so thateach pair of metal plates P can be soldered together with ease.

According to the above, the gas-liquid circulation device disclosedherein uses the force of gravity acting on the liquid-state workingfluid to drive the gaseous-state working fluid as well as theliquid-state working fluid to circulate continuously in the device,thereby eliminating the need for an additional electromechanical drivingdevice.

The above is the detailed description of the present invention. However,the above is merely the preferred embodiment of the present inventionand cannot be the limitation to the implement scope of the presentinvention, which means the variation and modification according to thepresent invention may still fall into the scope of the invention.

What is claimed is:
 1. A gravity-driven gas-liquid circulation device,comprising: a condensation unit having an end connected to a gaseousphase input tube and another end connected to a liquid phase outputtube; and an evaporation unit comprising a thermally conductive base forcontact with an external high-temperature device, a plurality of finsintegrally formed on the thermally conductive base, and an integrallyformed sealing housing provided on the thermally conductive base andenclosing the fins, wherein the integrally formed sealing housing isprovided with a gas outlet hole and a liquid inlet hole, the gas outlethole is lower than the gaseous phase input tube and is connected to anend of the gaseous phase input tube in order to guide a high-temperaturegaseous-state working fluid through the gaseous phase input tube to thecondensation unit, and the liquid inlet hole is level with or lower thanthe liquid phase output tube and is connected to an end of the liquidphase output tube in order to receive a liquid-state working fluid,allowing a force of gravity acting on the liquid-state working fluid toprovide a siphoning force and thereby cause circulation of theliquid-state working fluid and the gaseous-state working fluid.
 2. Thegravity-driven gas-liquid circulation device of claim 1, wherein thethermally conductive base is provided thereon with a reinforcementmember, wherein, the reinforcement member is clamped vertically betweenthe integrally formed sealing housing and the thermally conductive baseand serves to increase the compressive strength.
 3. The gravity-drivengas-liquid circulation device of claim 2, wherein the reinforcementmember is provided with at least one through hole and/or at least oneaperture to enable passage of the liquid-state working fluid.
 4. Thegravity-driven gas-liquid circulation device of claim 1, wherein theintegrally formed sealing housing includes a first housing portion and asecond housing portion; the first housing portion is provided on thethermally conductive base and encloses the fins; and, the second housingportion is integrally formed with, and lies on top of, the first housingportion.
 5. The gravity-driven gas-liquid circulation device of claim 1,wherein the top sides of the fins are higher than the bottom edge, andlower than the top edge, of the liquid inlet hole or are higher than thetop edge of the liquid inlet hole.
 6. The gravity-driven gas-liquidcirculation device of claim 1, wherein the gas outlet hole has a largerhole diameter than the liquid inlet hole.
 7. The gravity-drivengas-liquid circulation device of claim 1, wherein the spacing betweeneach two adjacent fins forms a flow channel, and the spacing ranges from0.2 mm to 1 mm.
 8. The gravity-driven gas-liquid circulation device ofclaim 7, wherein the liquid inlet hole is in alignment with the flowchannels.
 9. The gravity-driven gas-liquid circulation device of claim1, wherein the fins are integrally formed on the thermally conductivebase by a relieving means.
 10. The gravity-driven gas-liquid circulationdevice of claim 1, wherein each fin has a thickness ranging from 0.2 mmto 1 mm.
 11. The gravity-driven gas-liquid circulation device of claim1, wherein the condensation unit comprises a front condensationassembly, a rear condensation assembly, and a plurality of heatdissipation fins; the front condensation assembly comprises a front leftflow tube, a front right flow tube, and a plurality of front heatdissipation tubes; the front left flow tube and the front right flowtube are provided on two opposite lateral sides of the frontcondensation assembly respectively and are connected to the gaseousphase input tube and the liquid phase output tube respectively; thefront heat dissipation tubes are in communication with the front leftflow tube and the front right flow tube and are vertically spaced apart;the rear condensation assembly comprises a rear left flow tube, a rearright flow tube, and a plurality of rear heat dissipation tubes; therear left flow tube and the rear right flow tube are provided on twoopposite lateral sides of the rear condensation assembly respectively;the rear heat dissipation tubes are in communication with the rear leftflow tube and the rear right flow tube and are vertically spaced apart;gaps between the rear heat dissipation tubes and gaps between the frontheat dissipation tubes correspond to each other and jointly form aplurality of through grooves; the heat dissipation fins are in contactwith surfaces of the front heat dissipation tubes and surfaces of therear heat dissipation tubes to enable heat exchange between the heatdissipation fins and the heat dissipation tubes; the front left flowtube and the rear left flow tube are separately formed; and, the frontright flow tube and the rear right flow tube are separately formed. 12.The gravity-driven gas-liquid circulation device of claim 1, wherein thecondensation unit comprises a front condensation assembly, a rearcondensation assembly, and a plurality of heat dissipation fins; thefront condensation assembly comprises a front left flow tube, a frontright flow tube, and a plurality of front heat dissipation tubes; thefront left flow tube and the front right flow tube are provided on twoopposite lateral sides of the front condensation assembly respectivelyand are connected to the gaseous phase input tube and the liquid phaseoutput tube respectively; the front heat dissipation tubes are incommunication with the front left flow tube and the front right flowtube and are vertically spaced apart; the rear condensation assemblycomprises a rear left flow tube, a rear right flow tube, and a pluralityof rear heat dissipation tubes; the rear left flow tube and the rearright flow tube are provided on two opposite lateral sides of the rearcondensation assembly respectively; the rear heat dissipation tubes arein communication with the rear left flow tube and the rear right flowtube and are vertically spaced apart; gaps between the rear heatdissipation tubes and gaps between the front heat dissipation tubescorrespond to each other and jointly form a plurality of throughgrooves; the heat dissipation fins are in contact with surfaces of thefront heat dissipation tubes and surfaces of the rear heat dissipationtubes to enable heat exchange between the heat dissipation fins and theheat dissipation tubes; the front left flow tube and the rear left flowtube are jointly formed by two stamped plates; and, the front right flowtube and the rear right flow tube are jointly formed by two stampedplates.
 13. The gravity-driven gas-liquid circulation device of claim11, wherein at least one left opening is provided between the front leftflow tube and the rear left flow tube; at least one right opening isprovided between the front right flow tube and the rear right flow tube;and, the left opening and the right opening are diagonally arranged withrespect to each other, wherein the bottom side of the left opening ishigher than the top side of the right opening.
 14. The gravity-drivengas-liquid circulation device of claim 11, wherein both the front heatdissipation tube and the rear heat dissipation tube have a flattenedconfiguration.
 15. The gravity-driven gas-liquid circulation device ofclaim 11, wherein the front heat dissipation tube is provided thereinwith a plurality of supporting ribs, which extend through the front heatdissipation tube; and, the rear heat dissipation tube is providedtherein with a plurality of supporting ribs, which extend through therear heat dissipation tube.
 16. The gravity-driven gas-liquidcirculation device of claim 11, wherein a plurality of microstructuresare provided on the surface of each heat dissipation fin to increase thearea of contact between each heat dissipation fin and air.
 17. Thegravity-driven gas-liquid circulation device of claim 11, wherein theheat dissipation fins have a corrugated configuration or a serratedconfiguration.
 18. The gravity-driven gas-liquid circulation device ofclaim 1, wherein the condensation unit includes a plurality ofcondensation plate assemblies and a plurality of heat dissipation tins;the condensation plate assemblies are vertically spaced apart; the heatdissipation fins are inserted between the condensation plate assembliesand are therefore also spaced apart from one another; and, eachcondensation plate assembly is provided with a left flow tube on theleft side, a right flow tube on the right side, and a flow passage incommunication with the left flow tube and the right flow tube, whereinthe left flow tube and the right flow tube are connected to the gaseousphase input tube and the liquid phase output tube respectively.
 19. Thegravity-driven gas-liquid circulation device of claim 18, wherein eachcondensation plate assembly is formed by two metal plates; wherein, eachmetal plate is provided with a plurality of protruding structures on theside facing the flow passage in order to increase the strength of thecondensation plate assembly.